CN103124873B - Control valve - Google Patents
Control valve Download PDFInfo
- Publication number
- CN103124873B CN103124873B CN201180045516.2A CN201180045516A CN103124873B CN 103124873 B CN103124873 B CN 103124873B CN 201180045516 A CN201180045516 A CN 201180045516A CN 103124873 B CN103124873 B CN 103124873B
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- China
- Prior art keywords
- valve
- mentioned
- spool
- control valve
- adjusting member
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
- F16K31/42—Actuating devices; Operating means; Releasing devices actuated by fluid by means of electrically-actuated members in the supply or discharge conduits of the fluid motor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
- F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
- F16K11/04—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only lift valves
- F16K11/044—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only lift valves with movable valve members positioned between valve seats
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
- F16K31/04—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
- F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
- F16K31/36—Actuating devices; Operating means; Releasing devices actuated by fluid in which fluid from the circuit is constantly supplied to the fluid motor
- F16K31/40—Actuating devices; Operating means; Releasing devices actuated by fluid in which fluid from the circuit is constantly supplied to the fluid motor with electrically-actuated member in the discharge of the motor
- F16K31/402—Actuating devices; Operating means; Releasing devices actuated by fluid in which fluid from the circuit is constantly supplied to the fluid motor with electrically-actuated member in the discharge of the motor acting on a diaphragm
- F16K31/404—Actuating devices; Operating means; Releasing devices actuated by fluid in which fluid from the circuit is constantly supplied to the fluid motor with electrically-actuated member in the discharge of the motor acting on a diaphragm the discharge being effected through the diaphragm and being blockable by an electrically-actuated member making contact with the diaphragm
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
- F16K31/36—Actuating devices; Operating means; Releasing devices actuated by fluid in which fluid from the circuit is constantly supplied to the fluid motor
- F16K31/40—Actuating devices; Operating means; Releasing devices actuated by fluid in which fluid from the circuit is constantly supplied to the fluid motor with electrically-actuated member in the discharge of the motor
- F16K31/406—Actuating devices; Operating means; Releasing devices actuated by fluid in which fluid from the circuit is constantly supplied to the fluid motor with electrically-actuated member in the discharge of the motor acting on a piston
- F16K31/408—Actuating devices; Operating means; Releasing devices actuated by fluid in which fluid from the circuit is constantly supplied to the fluid motor with electrically-actuated member in the discharge of the motor acting on a piston the discharge being effected through the piston and being blockable by an electrically-actuated member making contact with the piston
Abstract
A control valve (1) of some mode is provided with: a body (5) that comprises a lead-in port (20) through which a refrigerant is led in from the upstream side, a lead-out port (22) through which the refrigerant is led out to the downstream side, a valve hole (28) through which the lead-in port (20) and the lead-out port (22) communicate with each other; a flexible valve element (66) that is attached to and detached from a valve seat (30) provided in an opening of the valve hole (28) to thereby open and close a valve part; a solenoid (4) that drives the valve element (66) in the direction in which the valve part is opened and closed; a pressure receiving element (57) that is disposed to face the valve element (66), operates integrally with the valve element (66), and receives pressure in a valve-closed direction by the surface thereof facing the valve element (66); and a flexible seal member (56) that is closely attached to the pressure receiving element (57) when the valve part is brought into a valve-closed state to thereby increase the effective pressure receiving area thereof.
Description
Technical field
The present invention relates to control fluid from the upstream side mobile control valve of side downstream.
Background technique
Usually, compressor, condenser, vaporizer etc. are configured in refrigerant circulation passage and form Vehicular air conditioner.And, for carrying out being provided with various control valves (for example, with reference to patent documentation 1) with the switching of the corresponding refrigerant circulation passage of operating condition of such refrigeration cycle, adjustment of cold medium flux etc.Such control valve majority possesses the actuators such as electromagnetic element, so that can adjust aperture from outside electricity.
Technical paper formerly
Patent documentation
(patent documentation 1) Japanese kokai publication hei 11-287354 communique
Summary of the invention
Invent problem to be solved
Such control valve has spool in the inside of main body, by actuator, drives this spool to come open and close valve portion.Also the promising driving force that makes this actuator acts on spool efficiently and has the control valve of the elimination structure of the pressure of eliminating the refrigerant that acts on spool.But, sometimes due to for preventing the existence of sewing the sealing component of establishing of the refrigerant in spool when work, and do not realize closely such elimination structure or limited the work responsiveness of spool, the leeway being improved in this.
One object of the present invention is to provide that a kind of work responsiveness of the driving force for actuator is good, the control valve of practical function accurately.
For solving the means of problem
For solving above-mentioned problem, the control valve of a scheme of the present invention comprises: main body, comprises the valve opening that imports export mouth, connection introducing port and the export mouth of the introducing port of fluid, the fluid of side derivation downstream from upstream side; There is flexible spool, by contacting/be located away from the valve seat of the opening portion of being located at valve opening, come open and close valve portion; Actuator drives spool in the switching direction of valve portion; Compression zone, relatively configures with spool, moves integratedly, and on the opposing side with spool, bear the pressure with spool opposite direction with spool; And there is flexible pressurized adjusting member, in valve portion, become while closing valve state and be close to compression zone and expand its effective compression area.
At this, the part of the contact of " spool "/be located away from valve seat has flexible, can consist of elastomer.The part of being close to compression zone of " pressurized adjusting member " has flexible, can consist of elastomer.
By this scheme, along with because spool dropping place becomes larger than valve opening in its effective compression area of valve seat, pressurized adjusting member is close to compression zone, and thus, effective compression area of the combination of compression zone and pressurized adjusting member is extended.That is, the impact that acts on the pressure of spool when closing valve becomes large, and the impact that antagonism ground acts on the pressure of compression zone therewith becomes greatly.Its result, can eliminate the impact of the pressure that acts on spool accurately.Thus, can improve the work responsiveness of spool to the driving force of actuator.
Invention effect
By the present invention, can provide a kind of work responsiveness of the driving force for actuator good, the control valve of practical function accurately.
Accompanying drawing explanation
Fig. 1 means the sectional drawing of structure of the control valve of the 1st mode of execution.
Fig. 2 means the part amplification profile of the pressure elimination structure of valve driving body.
Fig. 3 means the explanatory drawing of the operating state of control valve.
Fig. 4 means the sectional drawing of concrete structure of the control valve of the 2nd mode of execution.
Fig. 5 is the part enlarged view of Fig. 4.
Fig. 6 means the explanatory drawing of the operating state of control valve.
Fig. 7 means the explanatory drawing of the operating state of control valve.
Embodiment
Referring to accompanying drawing, describe embodiments of the present invention in detail.In addition, in the following description, for convenient, the illustrated state of sometimes take shows position relationship as benchmark.
［ the 1st mode of execution ］
Fig. 1 means the sectional drawing of structure of the control valve of the 1st mode of execution.Fig. 2 means the part amplification profile of the pressure elimination structure of valve driving body.
The control valve 1 of present embodiment is located at the bifurcation point of the refrigerant circulation passage of Vehicular air conditioner, as switching the mobile switching valve of refrigerant that flows to each difference passage in downstream side from upstream side passage, forms.That is, control valve 1 is first directed at the refrigerant by importing from upstream side passage any one of the 1st downstream side passage or the 2nd downstream side passage.
As shown in Figure 1, assembling is inner has accommodated the valve body 2 of valve system and has driven the electromagnetic element 4 of this valve system to form control valve 1.In the main body 5 of valve body 2, be equipped with: main valve 6, is switched to the flow direction of the refrigerant from upstream side passage in the 1st downstream side passage or the 2nd downstream side passage; Pilot valve 8, the open and-shut mode of control main valve 6.
Resinous the 2nd main body 14 is embedded in the first half of metal the 1st main body 12 coaxially, forms thus main body 5.The central part of a side of the 1st main body 12 is provided with the introducing port 20 that is communicated in upstream side passage.The top of the side of the opposition side of the 1st main body 12 is provided with the export mouth 22(that is communicated in the 1st downstream side passage and is equivalent to " the 1st export mouth "), bottom is provided with the export mouth 24(that is communicated in the 2nd downstream side passage and is equivalent to " the 2nd export mouth ").
The 2nd main body 14 has more downwards the more main body of the ladder barrel shape of path, is pressed into one heart the 1st main body 12.The upper end portion of the 2nd main body 14 is equipped with barrier film 25, is embedded with O ring 27 on the outer circumferential face of underpart.Thus, prevent that Jie from being sewed by the refrigerant in the gap of the 1st main body 12 and the 2nd main body 14.The inner peripheral surface of the Lower Half of the 2nd main body 14 forms bullport 26, and its underpart has formed valve opening 28(and has been equivalent to " the 1st valve opening ").In addition, by the lower ending opening edge of the 2nd main body 14, form valve seat 30(and be equivalent to " the 1st valve seat ").The lower ending opening portion of the 2nd main body 14 is communicated in introducing port 20.In addition the intercommunicating pore with being formed with on opposing side export mouth 22 inside and outside being communicated with the 2nd main body 14.By the inner passage that is communicated with introducing port 20, valve opening 28 and export mouth 22, formed the 1st passage that is communicated with upstream side passage and the 1st downstream side passage.
Connection introducing port 20 in the 1st main body 12 and the interconnecting part of export mouth 24 are provided with the valve seat forming portion 34 of concavo-convex (Emboss) shape.Valve seat forming portion 34 is side-prominent to the 2nd main body 14, and its inner side is formed with valve opening 36(and is equivalent to " the 2nd valve opening ").In addition, by the upper end open edge of valve seat forming portion 34, form valve seat 38(and be equivalent to " the 2nd valve seat ").By the inner passage that is communicated with introducing port 20, valve opening 36 and export mouth 24, formed the 2nd passage that is communicated with upstream side passage and the 2nd downstream side passage.
The inner side of main body 5 is equipped with valve driving body 41.Valve driving body 41 comprises: the valve of ladder barrel shape forms member 42, from the central part of main body 5, runs through valve opening 28,36 ground extensions; And valve seat formation member 43 cylindraceous, be set as and run through valve formation member 42.The upper end portion of valve driving body 41 is connected in barrier film 25 and fixture 44.Barrier film 25 possesses the main body with flexible plectane film-form, and its peripheral edge portion supports in the mode of being seized on both sides by the arms by main body 5 and electromagnetic element 4, and central part forms be fixed device 44 and valve the mode that member 42 folds and supports.The peripheral edge portion of barrier film 25 and central part are heavy wall shape, as sealing component, play a role.
Barrier film 25 plays a role as " the division portion " that be hyperbaric chamber 46 and back pressure chamber 48 by the internal separation of main body 5.The upper end portion that valve seat forms member 43 run through barrier film 25 and fixture 44 central part to back pressure chamber 48, extend.Fixture 44 is round-ended cylinder shape, in its bottom surface and between above valve formation member 42, clips and supports barrier film 25.Fixture 44 is fixed on barrier film 25 by snap ring (snap ring) (clasp) and valve seat forms member 43.As illustrated, the upper end open portion engaging by fixture 44, below electromagnetic element 4, carrys out limiting valve driving body 41 movement upward.In addition, fixture 44 is provided with small the sewing of section (leak) passage 50 that runs through barrier film 25 connection hyperbaric chambers, ground 46 and back pressure chamber 48.
Central part on the length direction of valve driving body 41 is provided with the flange part 52(extending outwardly along radial direction and plays a role as " compression zone "), be supported on slidably the bullport 26 of the 2nd main body 14.Above flange part 52, be formed with the ring-type engaging portion 54 of concavity.On the other hand, the sealing component 56(that the upper end central opening portion of the 2nd main body 14 is equipped with ring-type (ring) plays a role as " pressurized adjusting member ").In the present embodiment, sealing component 56 consists of the barrier film of film-form, and its peripheral edge portion is clipped to be supported between the 2nd main body 14 and the fixed component 58 of ring-type.In addition, in the central opening portion of sealing component 56, be equipped with the engaging portion 60 of concavo-convex (thin pearl (bead)) downwards, be constituted as and can engaging in valve, form the ring-type engaging portion 54 of member 42.
Fixed component 58 consists of resin material, and below it, inner periphery is subjected to fillet processing, even if make to contact with sealing component 56, also can not damage it.By snap ring (positioning ring), prevent that fixed component 58 from coming off from the 2nd main body 14.Flange part 52 and sealing component 56 as divide the 2nd main bodys 14 Lower Half " division portion " and play a role.On the other hand, near the periphery of the 2nd main body 14, be formed with the communicating passage 80 that is communicated with introducing port 20 and hyperbaric chamber 46.
The underpart that valve forms member 42 is provided with along radial direction outstanding flange part 62 outwardly, and the outer circumferential face of this flange part 62 is embedded with the spool consisting of the elastomer of ring-type (being rubber in the present embodiment) and forms member 64.The upper end portion formation spool 66(that spool forms member 64 is equivalent to " the 1st spool "), it contacts/is located away from valve seat 30 and opens and closes the 1st passage.In addition, the underpart formation spool 68(that spool forms member 64 is equivalent to " the 2nd spool "), it contacts/is located away from valve seat 38 ground and opens and closes the 2nd passages.From flange part 62, extend downwards and be provided with a plurality of 70(of foot and only represent in the figure 1), by the inner peripheral surface of valve opening 36, supported slidably.Valve driving body 41 is supported on mode stably action in the switching direction of valve portion of the inner peripheral surface of main body 5 slidably with flange part 52He foot 70.
Valve seat forms member 43 and is inserted by the axis along valve formation member 42, and its upper end portion is formed guide's valve opening 72 by tube reducing.And the upper-end surface that is formed member 43 by valve seat forms guide's valve seat 74.In addition, back pressure chamber 48 is equipped with the guide's spool 76 being driven by electromagnetic element 4.It is rubber in the present embodiment that guide's spool 76 is equipped with elastomer 77(in its lower end central authorities), contact/be located away from guide's valve seat 74 ground and open and close pilot valve 8.Guide's valve opening 72 is formed on a part for the leader channel 78 that inner side that valve seat forms member 43 forms.Valve seat forms member 43 and is extended and arrange as illustrated, even if make valve driving body 41 in top dead center, its lower ending opening portion also locates more on the lower than valve seat 38.
In structure as described above, the pressure P 1(of the upstream side importing from introducing port 20 is called " upstream side pressure P 1 ") the 1st passage, through main valve 6, become pressure P 2(and be called " downstream side pressure P 2 "), on the other hand, in the 2nd passage, through main valve 6, become pressure P 3(and be called " downstream side pressure P 3 ").In addition, upstream side pressure P 1 is imported into hyperbaric chamber 46 by communicating passage 80, along with become intermediate pressure Pp in back pressure chamber 48 by sewing passage 50, and then becomes downstream side pressure P 3 through pilot valve 8.
At this, as shown in Figure 2, in the present embodiment, because the effective diameter A of valve opening 28 and valve opening 36 and the effective diameter B of bullport 26 are set to, equate (because effective compression area of flange part 62 and effective compression area of flange part 52 are set as substantially, equating), the impact of pretending for the downstream side pressure P 2 of valve driving body 41 is eliminated.Especially, be provided with sealing component 56 and tightly realized this pressure and eliminated.That is, because of spool 66 the 1st valve portion, becoming while closing valve state as illustrated, sealing component 56 be close to below flange part 52 above, realize the pressurized regulation structure of effective compression area of compression body 57 expanding as their combination.
That is, effective compression area of spool 66 is set to corresponding with the effective diameter A of valve opening 28.But, in spool 66 dropping places as illustrated under the complete sealing state of valve seat 30, because forming spool 66(and spool 68) elastomeric character (distortion), the effective diameter A(that actual effective pressurized diameter A ' is slightly larger than valve opening 28 is with reference to double dot dash line in figure).For correspondingly, when this seals completely, make flange part 52 be close to above sealing component 56 below, the effective diameter B(that makes thus the effective pressurized diameter B ' in the face of the compression body 57 of spool 66 be slightly larger than bullport 26 is consistent with the double dot dash line in figure).
Specifically, effectively pressurized diameter B ' as illustrated, becomes peripheral part at sealing component 56 be fixed member 58 and the 2nd main body 14 diameter C of interior Zhou Duan of clamping and the mid diameter of the external diameter B of flange part 52 (B '=B+C/2).When the 1st valve portion closes valve, effective pressurized diameter A ' of spool 66 is identical with effective pressurized diameter B ' of compression body 57, realizes the complete pressure of downstream side pressure P 2 and eliminates.Thus, when electromagnetic element 4 has been closed, the rapid dropping place of spool 66, in valve seat 30, makes the 1st valve portion to be closed to valve reliably.
In addition, at electromagnetic element 4, be unlocked and spool 66 while having moved to valve opening position (spool 68 is to closing valve direction while having moved), being disengaged with the state of being close to above of flange part 52 below of sealing component 56.Therefore, effective pressurized diameter A of spool 66 becomes and equates with effective pressurized diameter B of compression body 57, realizes pressure and eliminates.The potential energy that spool 66 is given because of electromagnetic element 4 moves rapidly to valve opening position.
When the 1st valve portion drives valve, sealing component 56 below with being stripped from its peripheral edge portion above of flange part 52, therefore the displacement that sealing component 56 can limiting valve driving body 41.That is, though sealing component 56 is compression members (barrier film) of film-form, compare with for example bellows (bellows), also can favorably obtain the stroke (stroke) of larger valve driving body 41.In addition, the slip surface of valve driving body 41 and the 2nd main body 14 is not provided with the sealing components such as O ring, therefore can make the slip resistance of valve driving body 41 very little.Therefore,, even if it is less to act on the driving force (electromagnetic element power) of valve driving body 41, also can make valve driving body 41 action smoothly in the switching direction of valve portion.That is, the differential pressure that acts on valve driving body 41 be eliminated and slip resistance less, therefore it is less to be used in the driving force of open and close control valve 1, the also responsiveness of the open and close controlling of retentive control valve 1 well.
Return to Fig. 1, electromagnetic element 4 comprises the core 84(fixed iron core of the ladder barrel shape that the mode with the upper end open portion of sealed body 5 is mounted), and be assembled as the sleeve that has round-ended cylinder shape 86 of the first half of accommodating core 84.In sleeve 86, plunger (plunger) 88(moving core) to be accommodated with the mode of core 84 relative configuration on axial direction.The peripheral part of sleeve 86 is provided with coil rack 90, on this coil rack 90, is wound with electromagnetic coil 92.And, to cover the mode of electromagnetic coil 92 from outside, be provided with shell 94.Sleeve 86 runs through shell 94 on axial direction.The electrical wiring harness 96 of energising use is drawn from electromagnetic coil 92.
Plunger 88 is cylindric, and its Lower Half is pressed into the upper end portion of working beam 98.Working beam 98 is cylindric, runs through core 84 and is linked to guide's spool 76.That is, guide's spool 76 is set as to be situated between and forms one by working beam 98 and plunger 88.That is, guide's spool 76 moves integratedly with plunger 88.The spring 99 of giving potential energy to guide's spool 76 on valve opening position is situated between and is loaded between core 84 and plunger 88 by plunger 88.
The control valve 1 forming is as described above as playing a role according to the control valve of guide's operation type that the "on" position of electromagnetic element 4 is switched to the path of refrigerant.Below describe its action in detail.Fig. 3 means the explanatory drawing of the operating state of control valve.Fig. 3 has represented the "on" position after electromagnetic element 4 is unlocked.In addition the Fig. 1 having illustrated, has represented the non-power status after electromagnetic element 4 is closed.
As shown in Figure 1, under the pent state of electromagnetic element 4, electromagnetic element power does not produce effect, therefore give potential energy by 99 pairs of guide's spools 76 of spring on valve opening position, pilot valve 8 becomes out valve state.Now, the cold media of back pressure chamber 48 exports to downstream side by leader channel 78, and intermediate pressure Pp reduces, therefore valve driving body 41 is given potential energy upward by upstream side pressure P 1 and the differential pressure (P1-Pp) of intermediate pressure Pp.Thus, about main valve 6, spool 66 becomes the valve state that closes, and spool 68 becomes out valve state.Its result, realization the 2nd passage is as illustrated opened, the pent state of the 1st passage.That is the refrigerant, importing from upstream side passage is derived to bypass channel from export mouth 24.
On the other hand, if electromagnetic element 4 is unlocked, because electromagnetic element power attraction force acts is between plunger 88 and core 84, therefore guide's spool 76 is given potential energy to closing valve direction, pilot valve 8 becomes the valve state that closes.Now, refrigerant is situated between and is imported into by sewing passage 50 from upstream side, therefore intermediate pressure Pp becomes upstream side pressure P 1.Now, the pressure that acts on the refrigerant of valve driving body 41 is eliminated, and the slip resistance between valve driving body 41 and main body 5 is also less, therefore valve driving body 41 is driven smoothly by electromagnetic element power.Its result, about main valve 6, spool 66 becomes out rapidly valve state, and spool 68 becomes rapidly the valve state that closes.That is, the 1st passage is opened and the pent state of the 2nd passage is implemented as illustrated, and the refrigerant importing from upstream side passage is derived to condenser from export mouth 22.
［ the 2nd mode of execution ］
Next, the 2nd mode of execution of the present invention is described.The control valve of present embodiment is that its aperture is adjusted to the Proportional valve of setting aperture, and actuator consists of stepper motor, in addition, be not to adopt three-way valve but adopt two-way valve to form in this point different from the 1st mode of execution.Fig. 4 means the sectional drawing of concrete structure of the control valve of the 2nd mode of execution.Fig. 5 is the part enlarged view of Fig. 4.(A) the C portion enlarged view of presentation graphs 4, (B) the D portion enlarged view of presentation graphs 4.
The supply current value that the aperture of the control valve 201 of present embodiment is adjusted to adaptively with to actuator is set aperture accordingly.Control valve 201 is substantially controlled as full-gear, heavy caliber state of a control, small-bore state of a control, closes the arbitrary state in valve state.In addition, heavy caliber state of a control is not reach full-gear but the larger state of aperture, and small-bore state of a control is not reach to close valve state but the less state of aperture.Control valve 201, by small-bore control, also plays a role as expansion gear.
As shown in Figure 4, control valve 201 is constituted as stepping motor driving type mortor operated valve, by being situated between, connector element 103 assembled valve main bodys 101 and electric motor units 102, consists of.Valve body 101 is constituted as, and accommodates coaxially small-bore the 1st valve 105(and open and close " the 1st valve portion " in having the main body 104 of bottom tube-like) and bigbore the 2nd valve 106(switching " the 2nd valve portion ").
Resinous the 2nd main body 108 is embedded in coaxially metal the 1st main body 107 and forms main body 104.A sidepiece of the 1st main body 107 is provided with introducing port 110, and the other side is provided with export mouth 112.
The 2nd main body 108 has more downwards the more ladder barrel shape main body of path, and ladder barrel shape main body is pressed into the 1st main body 107 with one heart.On the face relative with introducing port 110 in the 2nd main body 108 and the face relative with export mouth 112, be respectively equipped with and be communicated with inside and outside intercommunicating pore.Be equipped with O ring 114, make to seal near these intercommunicating pores.
Between the 2nd main body 108 and connector element 103, be equipped with discoideus division member 116.The peripheral edge portion of dividing member 116 supports in the mode that is connected member 103 and the 2nd main body 108 and folds, and divides the inside of valve body 101 and the inside of electric motor units 102.The central part of dividing member 116 is provided with the bearing portion 118 of concavo-convex (Emboss) shape.The inner peripheral surface of bearing portion 118 is provided with female thread portion 120, and outer circumferential face plays a role as sliding bearing.Annular seal member 122 is loaded on connector element 103 and divides between member 116.The Lower Half of the 2nd main body 108 is by path.And the inner peripheral surface of its Lower Half is capable becomes bullport 124, its upper end portion forms valve opening 126(and is equivalent to " the 2nd valve opening ").In addition, by the upper end open end margin of valve opening 126, form valve seat 128(and be equivalent to " the 2nd valve seat ").
The spool 130(in large footpath is equivalent to " the 2nd spool "), the spool 132(of path is equivalent to " the 1st spool ") and valve working body 134 be equipped on coaxially the inside of main body 104.Spool 130 engages and is located away from valve opening 126 and opens and closes bigbore the 2nd valve portion from upstream side.The outer circumferential face of spool 130 is embedded with the valve member 136 for example, consisting of the elastomer of ring-type (rubber), by this valve member 136, falls to being seated at valve seat 128, can close the 2nd valve portion completely.Be provided with the shoulder hole that runs through the centre of spool 130 along axial direction, the valve seat that its upper end open portion is pressed into ring-type forms member 138.
The interior perimembranous that forms member 138 by valve seat forms valve opening 140(and is equivalent to " the 1st valve opening "), by its upper end open end margin, form valve seat 142(and be equivalent to " the 1st valve seat ").Valve seat forms member 138 and for example, consists of metal body (stainless steel), by spool 132, falls to being seated at valve seat 142, can close the 1st valve portion.As illustrated, in the upstream side formation of valve opening 126 and valve opening 140, be communicated in the hyperbaric chamber 115 of introducing port 110, in the downstream side of valve opening 126 and valve opening 140, be formed with the low pressure chamber 117 that is communicated in export mouth 112.
The 144(of division portion plays a role as " compression zone ") being situated between is connected with in spool 130 by tube reducing portion.Division portion 144 is configured in low pressure chamber 117.And the underpart of division portion 144 is supported on bullport 124 slidably, guarantee thus the stable operation to switching direction of spool 130.Between division portion 144 and the bottom of main body 104, form back pressure chamber 146.In addition, form the communicating passage 148 that connects spool 130 and division portion 144, hyperbaric chamber 115 is communicated with back pressure chamber 146.Thus, in back pressure chamber 146, be always full of the upstream side pressure P 1 importing from introducing port 110.
In the present embodiment, because the effective diameter A of valve opening 126 and the effective diameter B of bullport 124 are set to, equate (because effective compression area of spool 130 and effective compression area of division portion 144 are set as substantially, equating), the impact of pretending for the upstream side pressure P 1 of spool 130 is eliminated.Especially, for realizing closely this pressure, eliminate, below the division portion 144 in back pressure chamber 146, be equipped with in the 2nd valve portion and when closing valve state, be close to division portion 144 and expand the pressurized adjusting member 149 of its effective compression area.Pressurized adjusting member 149 for example, consists of film-form elastomer (rubber) in the form of a ring, and the heavy section of its peripheral end is supported in the mode being sandwiched between the 1st main body 107 and the 2nd main body 108.
That is,, as shown in Fig. 5 (A), effective compression area of spool 130 is set to corresponding with the effective diameter A of valve opening 126.But under the complete sealing state of valve seat 128, because of elastomeric character, the actual effectively effective diameter A(that pressurized diameter A ' is slightly larger than valve opening 126 is with reference to double dot dash line in figure in valve member 136 dropping places as illustrated).For correspondingly, as shown in Fig. 5 (B), when this seals completely, pressurized adjusting member 149 is close to below division portion 144, the effective diameter B(that makes thus effective pressurized diameter B ' of back pressure chamber 146 sides be slightly larger than bullport 124 is consistent with the double dot dash line in figure).By making like this effective compression area of spool 130 and effective compression area of division portion 144 equate, realized pressure completely and eliminated.
Get back to Fig. 4, the upper end portion of spool 130 is provided with discoideus spring bracket member 150.Spring bracket member 150 is provided with the intercommunicating pore 151 for refrigerant is passed through.And, to closing the spring 152(that valve direction gives potential energy to spool 130, be equivalent to " giving potential energy member ") be loaded on spring bracket member 150 and divide between member 116.On the other hand, the spring 154(that Jie gives potential energy to valve opening position to spool 130 by division portion 144 is equivalent to " giving potential energy member ") be loaded between division portion 144 and main body 104.In addition in the present embodiment, by the load setting of spring 152, be the load that is greater than spring 154.
It is cylindric that spool 132 is ladder, and its Lower Half runs through spring bracket member 150 and relatively configures with valve opening 140, and the first half is by 134 supportings of valve working body.Spool 132 is constituted as so-called aciculiform spool, and its sharp-pointed front end is touched/is located away from valve opening 140.And spool 132 is touched/is located away from valve seat 142, the 1st valve portion is opened and closed thus.Valve working body 134 is run through in the upper end portion of spool 132, and its front end is become engaging portion 156 by outside rivet clasp.
Valve working body 134 is ladder barrel shape, and its peripheral part is formed with outer screw section 158.Outer screw section 158 is screwed together in the female thread portion 120 of bearing portion 118.The upper end portion of valve working body 134 is provided with along radial direction outward extending a plurality of (being 4 in the present embodiment) foot 160, is embedded in the rotor of electric motor units 102.To closing the spring 162 that valve direction gives potential energy to spool 132, be loaded between valve working body 134 and spool 132.Under common state, as illustrated, by 162 pairs of spools 132 of spring, give potential energy downwards, on the other hand, the engaging portion 156 of spool 132 is engaged in the upper end portion of valve working body 134.Therefore, spool 132 become with respect to valve working body 134 most on the lower side state.
Valve working body 134 is subject to the rotary driving force of electric motor units 102 and rotates and its rotating force is transformed to and directly enters power.That is,, when 134 rotation of valve working body, by screw mechanism, valve working body 134 displacement on axial direction drives spool 132 in switching direction.When the 1st valve portion drives valve, spool 132 moves integratedly with valve working body 134.In the present embodiment, as illustrated, be designed to the limit position that closes valve direction (lower dead center) that can move to 134 of valve working bodies, the 1st valve portion just in time becomes the valve state that closes.But, even because of assembly error etc., before valve working body 134 is positioned at lower dead center, spool 132 becomes in valve seat 142, the 1 valve portions the valve state that closes with regard to dropping place, due to spool 132 can antagonistic spring 162 potential energy and with relatively displacement of valve working body 134, therefore also completely no problem.
On the other hand, adopt the stepper motor that comprises rotor 172 and stator 173 to form electric motor units 102.Electric motor units 102 is constituted as is having the inside of the sleeve 170 of round-ended cylinder shape can free rotary ground supporting rotor 172.Periphery at sleeve 170 is provided with the stator 173 of having accommodated field coil 171.The lower ending opening portion of sleeve 170 is situated between and is assembled in main body 104 by connector element 103, forms the main body of control valve 201 together with main body 104.
Rotor 172 possesses the magnet 176 that is formed running shaft 174 cylindraceous and is equipped on the periphery of this running shaft 174.In the present embodiment, magnet 176 is geomagnetic into 24 utmost points.
The inner side of running shaft 174 is formed with the inner space of the total length that roughly reaches electric motor units 102.The specific place of the inner peripheral surface of running shaft 174 is provided with the guide portion 178 extending in parallel with axis.Guide portion 178 is used to form the teat engaging with rotation stopper described later, the ridge extending in parallel with axis, consists of.
The underpart of running shaft 174 is by tube reducing slightly, and side face is provided with 4 guide portion 180 that extend in parallel with axis within it.Guide portion 180 consists of a pair of ridge of extending abreast with axis, on the inner peripheral surface of running shaft 174 every 90 degree arrange.4 foots 160 of above-mentioned valve working body 134 are embedded in this 4 guide portion 180, and rotor 172 can rotate integratedly with valve working body 134.But, although valve working body 134 is limited with respect to the Relative Displacement in the sense of rotation of rotor 172, allow along the displacement of the axial direction of this guide portion 180.That is, valve working body 134 is driven to rotatably the switching direction of spool 132 together with rotor 172.
In the inside of rotor 172, along its axis, be equipped with the axle 182 of strip.The upper end portion of axle 182 is pressed into the bottom center of sleeve 170, is fixed thus by single head, extends abreast with guide portion 178 in inner space.Axle 182 be configured in the same axis of valve working body 134 on.On axle 182, be provided with the spiral helicine guide portion 184 of roughly extending in its length range.Guide portion 184 by coiled type member form, by build-in in the outside of axle 182.The upper end portion of guide portion 184 is rolled and becomes engaging portion 186.
Spiral helicine rotation stopper 188 is rotatably sticked in guide portion 184.Rotation stopper 188 has the spiral helicine engagement portion 190 of guide portion of being sticked in 184 and is rotated the power transfering part 192 of axle 174 supportings.Engagement portion 190 is a circle coil shape, and its underpart is provided with along the outward extending power transfering part 192 of radial direction.The front end of power transfering part 192 is sticked in guide portion 178.That is, power transfering part 192 butts engaging are in a ridge of guide portion 178.Therefore, by running shaft 174, the Relative Displacement of sense of rotation is limited rotation stopper 188, but allows the displacement along its axial direction of slip in guide portion 178.
That is, rotation stopper 188 rotates integratedly with rotor 172, and its engagement portion 190, is driven by guide thus along guide portion 184 on axial direction.But the driving scope of the axial direction of rotation stopper 188 is formed on the engaging portion restriction at the two ends of guide portion 178.The figure shows the state of rotation stopper 188 in lower dead center.At rotation stopper 188, upward when displacement and 186 engaging of engaged portion, this position becomes top dead center.
The upper end portion of rotor 172 can free rotary ground supporting by axle 182, and underpart can free rotary ground supporting by bearing portion 118.Specifically, be provided with the end member 194 of round-ended cylinder shape with the upper end open portion of sealing rotary rotating shaft 174, the part of Cylindorical rod 196 that is arranged at the centre of this end member 194 is supported by axle 182.That is, bearing portion 118 becomes a distolateral bearing portion, and the slide part with Cylindorical rod 196 in axle 182 becomes another distolateral bearing portion.
The control valve 201 forming is as described above as regulating the control valve of the stepper motor operating type of its valve opening to play a role by the driving control of electric motor units 102.Below describe its action in detail.
Fig. 6 and Fig. 7 mean the explanatory drawing of the working state of control valve.Fig. 6 has represented the full-gear of the 1st valve portion, and Fig. 7 has represented the full-gear of the 2nd valve portion.In addition the Fig. 4 having illustrated, has represented the valve state that closes of the 1st valve portion and the 2nd valve portion.
In the flow control of control valve 201, not shown control device calculates and the driving step number of setting the corresponding stepper motor of aperture, and driving current (driving pulse) is offered to field coil 171.Thus, rotor 172 rotations, on the one hand, valve working body 134 is driven in rotation, and the aperture of small-bore the 1st valve portion and heavy caliber the 2nd valve portion is adjusted to setting aperture, on the other hand, rotation stopper 188 is driven along guide portion 184, and the operating range of each spool is limited thus.
Specifically, while carrying out small-bore control when carrying out the specific heating installation operation of Dehumidification controlling etc., rotor 172 by one direction rotarily actuate (forward), spool 132 is to valve opening position displacement thus, the 1st valve portion becomes out valve state.That is, driven in the scope of spool 132 between the fully open position shown in the full-shut position shown in Fig. 4 and Fig. 6.In the present embodiment, when rotor 172 rotates 5 weeks from the valve state that closes of the 1st valve portion, the 1st valve portion becomes full-gear, and it is 0.5mm that spool 132 rises every 1 circle of 2.5mm(from valve seat 142).During this period, the valve opening of small-bore the 1st valve portion (Valve travel) changes pro rata.
In addition, when carrying out heavy caliber when Defrost operation etc. and controlling, the full-gear of rotor 172 in the 1st valve portion shown in Fig. 6 and further rotate up (forward) the party.As a result, spool 130 is pulled on and is driven to valve opening position by spool 132.Now, the engaging spool 132 because spring bracket member 150 becomes fixture, therefore to a certain extent, the aperture of the 1st valve portion (full-gear) is held certain.On the contrary, because spring bracket member 150 is pulled on together with spool 132, therefore the potential energy of giving by spring 154 makes spool 130 drive to valve opening position.
Now, driven in the scope of spool 130 between the fully open position shown in the full-shut position shown in Fig. 6 and Fig. 7.In the present embodiment, when rotor 172 rotates 7 weeks from the valve state that closes (full-gear of the 1st valve portion) of the 2nd valve portion, the 2nd valve portion becomes full-gear, and spool 130 is mentioned the every 1 circle 0.5mm of 3.5mm(from valve seat 128).That is, rotation stopper 188 is in 186 engagings of the engaged portion of top dead center position, and the rotation of result rotor 172 stops.During this period, the valve opening (Valve travel) of heavy caliber the 2nd valve portion changes pro rata.In addition, rotor 172 is during to opposite spin, spool 130 and spool 132 by step contrary to the above to closing the action of valve direction.Because the revolution of rotor 172 is corresponding with the driving step number as control command value.
The preferred embodiment of the present invention has more than been described, but the present invention is not limited to this specific mode of execution, certainly within the scope of technological thought of the present invention, can have various distortion.
The control valve that above-mentioned mode of execution relates to is suitable for being provided with the automobile-used cooling and warming unit of the automobile of internal-combustion engine, the automobile that the hybrid power type of internal-combustion engine and motor is installed simultaneously, electric vehicle etc., and it also can be applicable to automobile-used cooling and warming unit in addition certainly.In addition the control valve that, above-mentioned mode of execution relates to also can be applicable to the purposes beyond cooling and warming unit.For example, can be as not being to control flowing of refrigerant, but the mobile control valve of controlling water, oil, other working fluid is used.
Label declaration
1 control valve, 2 valve bodies, 4 electromagnetic elements, 5 main bodys, 6 main valves, 8 pilot valves, 20 introducing ports, 22,24 export mouths, 25 barrier films, 26 bullports, 28 valve openings, 30 valve seats, 36 valve openings, 38 valve seats, 41 valve driving bodies, 42 valves form member, 43 valve seats form member, 44 fixtures, 46 hyperbaric chambers, 48 back pressure chambers, 50 sew passage, 52 flange parts, 54 ring-type engaging portions, 56 sealing components, 57 compression bodies, 60 engaging portions, 62 flange parts, 64 spools form member, 66,68 spools, 72 guide's valve openings, 74 guide's valve seats, 76 guide's spools, 78 leader channels, 80 communicating passage, 84 iron cores, 88 plungers, 98 working beams, 101 valve bodies, 102 electric motor units, 104 main bodys, 105 the 1st valves, 106 the 2nd valves, 110 introducing ports, 112 export mouths, 115 hyperbaric chambers, 116 divide member, 117 low pressure chambers, 124 bullports, 126 valve openings, 128 valve seats, 130,132 spools, 134 valve working bodies, 136 valve members, 138 valve seats form member, 140 valve openings, 142 valve seats, 144 division portions, 146 back pressure chambers, 148 communicating passage, 149 pressurized adjusting member, 156 engaging portions, 172 rotors, 173 stators, 174 Hui Rotating Shaft, 176 magnets, 178,180 guide portion, 182 axles, 184 guide portion, 186 engaging portions, 188 rotation stoppers, 190 engaging portions, 192 power transfering parts, 201 control valves.
Claims (8)
1. a control valve, is characterized in that, comprising:
Main body, comprise from upstream side import the introducing port of fluid, downstream side derive fluid export mouth, be communicated with the valve opening of above-mentioned introducing port and above-mentioned export mouth,
There is flexible spool, by contacting/be located away from the valve seat of the opening portion of being located at above-mentioned valve opening, come open and close valve portion,
Actuator drives above-mentioned spool in the switching direction of above-mentioned valve portion,
Compression zone, relatively configures with above-mentioned spool, and move integratedly with above-mentioned spool, and on the opposing side with above-mentioned spool, bear the pressure with above-mentioned spool opposite direction, and
There is flexible pressurized adjusting member, in above-mentioned valve portion, become while closing valve state and be close to above-mentioned compression zone and expand its effective compression area.
2. control valve as claimed in claim 1, is characterized in that,
Above-mentioned pressurized adjusting member is supported in aforementioned body as follows: at above-mentioned spool, from closing valve state when opening valve state action, from above-mentioned compression zone, peel off at least partly, make to diminish with the area of contact of above-mentioned compression zone.
3. control valve as claimed in claim 1 or 2, is characterized in that,
Also comprise bullport, equate with the effective diameter of above-mentioned valve opening and be located at coaxially aforementioned body;
Above-mentioned compression zone is by can be along the supporting slidably in the switching direction of above-mentioned valve portion of above-mentioned bullport;
Above-mentioned pressurized adjusting member is equipped on the position different from the slip surface of above-mentioned compression zone in aforementioned body.
4. control valve as claimed in claim 1 or 2, is characterized in that,
Above-mentioned compression zone when above-mentioned valve portion closes valve state is constituted as and equates with effective compression area of the combination of above-mentioned pressurized adjusting member and effective compression area of above-mentioned spool.
5. control valve as claimed in claim 1 or 2, is characterized in that,
Above-mentioned pressurized adjusting member consists of barrier film.
6. control valve as claimed in claim 3, is characterized in that,
Above-mentioned compression zone when above-mentioned valve portion closes valve state is constituted as and equates with effective compression area of the combination of above-mentioned pressurized adjusting member and effective compression area of above-mentioned spool.
7. control valve as claimed in claim 3, is characterized in that,
Above-mentioned pressurized adjusting member consists of barrier film.
8. control valve as claimed in claim 4, is characterized in that,
Above-mentioned pressurized adjusting member consists of barrier film.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2010-221388 | 2010-09-30 | ||
| JP2010221388A JP5572809B2 (en) | 2010-09-30 | 2010-09-30 | Control valve |
| PCT/JP2011/004874 WO2012042745A1 (en) | 2010-09-30 | 2011-08-31 | Control valve |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103124873A CN103124873A (en) | 2013-05-29 |
| CN103124873B true CN103124873B (en) | 2014-10-29 |
Family
ID=45892241
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201180045516.2A Expired - Fee Related CN103124873B (en) | 2010-09-30 | 2011-08-31 | Control valve |
Country Status (5)
| Country | Link |
|---|---|
| EP (1) | EP2623827A4 (en) |
| JP (1) | JP5572809B2 (en) |
| KR (1) | KR20130137640A (en) |
| CN (1) | CN103124873B (en) |
| WO (1) | WO2012042745A1 (en) |
Families Citing this family (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6216923B2 (en) * | 2013-09-25 | 2017-10-25 | 株式会社テージーケー | Control valve |
| JP6218023B2 (en) * | 2013-09-25 | 2017-10-25 | 株式会社テージーケー | solenoid valve |
| JP6218024B2 (en) | 2013-09-25 | 2017-10-25 | 株式会社テージーケー | solenoid valve |
| JP2015075124A (en) * | 2013-10-04 | 2015-04-20 | 株式会社テージーケー | Electromagnetic valve |
| JP2016089969A (en) * | 2014-11-06 | 2016-05-23 | 株式会社テージーケー | solenoid valve |
| SE1500180A1 (en) * | 2015-04-14 | 2016-10-04 | Staccato Tech Ab | Valve Seat |
| JP6768193B2 (en) * | 2016-05-06 | 2020-10-14 | Toto株式会社 | Flow control valve |
| JP6772780B2 (en) * | 2016-11-23 | 2020-10-21 | アイシン精機株式会社 | Fluid control valve |
| JP2018084278A (en) * | 2016-11-23 | 2018-05-31 | アイシン精機株式会社 | Valve module |
| JP7087537B2 (en) * | 2018-03-26 | 2022-06-21 | 日本電産トーソク株式会社 | Solenoid valve and flow path device |
| JP7017498B2 (en) * | 2018-10-19 | 2022-02-08 | 株式会社鷺宮製作所 | solenoid valve |
| KR102192901B1 (en) * | 2019-06-26 | 2020-12-18 | 인지컨트롤스 주식회사 | Vehicle cooling water control module apparatus and control method thereof |
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|---|---|---|---|---|
| EP1338837B1 (en) * | 2002-02-21 | 2005-09-28 | TGK CO., Ltd. | Four-way switching valve |
| EP1586835A2 (en) * | 2004-04-13 | 2005-10-19 | Tgk Company, Ltd. | Fluid control valve |
| EP1396691B1 (en) * | 2002-09-05 | 2007-10-17 | TGK Co., Ltd. | Proportional valve |
| CN101166926A (en) * | 2005-04-27 | 2008-04-23 | 伊格尔工业股份有限公司 | Transfer valve |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4149565A (en) * | 1977-02-02 | 1979-04-17 | International Harvester Company | Pilot controlled poppet valve assembly |
| JPH0615289Y2 (en) * | 1988-01-29 | 1994-04-20 | 日産自動車株式会社 | Pressure control valve |
| JPH0557565U (en) * | 1992-01-14 | 1993-07-30 | 甲南電機株式会社 | solenoid valve |
| JP3145233B2 (en) * | 1992-08-07 | 2001-03-12 | 株式会社鷺宮製作所 | Two-way solenoid valve |
| JP3844321B2 (en) * | 1998-04-03 | 2006-11-08 | 株式会社テージーケー | Pilot operated three-way switching solenoid valve |
| DE29912814U1 (en) * | 1999-07-22 | 1999-12-02 | Buerkert Werke Gmbh & Co | Dispensing system for fuel pumps |
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2010
- 2010-09-30 JP JP2010221388A patent/JP5572809B2/en active Active
-
2011
- 2011-08-31 WO PCT/JP2011/004874 patent/WO2012042745A1/en active Application Filing
- 2011-08-31 CN CN201180045516.2A patent/CN103124873B/en not_active Expired - Fee Related
- 2011-08-31 KR KR1020137011188A patent/KR20130137640A/en not_active Application Discontinuation
- 2011-08-31 EP EP11828313.4A patent/EP2623827A4/en not_active Withdrawn
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1338837B1 (en) * | 2002-02-21 | 2005-09-28 | TGK CO., Ltd. | Four-way switching valve |
| EP1396691B1 (en) * | 2002-09-05 | 2007-10-17 | TGK Co., Ltd. | Proportional valve |
| EP1586835A2 (en) * | 2004-04-13 | 2005-10-19 | Tgk Company, Ltd. | Fluid control valve |
| CN101166926A (en) * | 2005-04-27 | 2008-04-23 | 伊格尔工业股份有限公司 | Transfer valve |
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Also Published As
| Publication number | Publication date |
|---|---|
| WO2012042745A1 (en) | 2012-04-05 |
| EP2623827A1 (en) | 2013-08-07 |
| JP5572809B2 (en) | 2014-08-20 |
| EP2623827A4 (en) | 2015-10-21 |
| KR20130137640A (en) | 2013-12-17 |
| JP2012077787A (en) | 2012-04-19 |
| CN103124873A (en) | 2013-05-29 |
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